JP2015017551A - Gas compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To prevent or suppress corrosion of an opening, in a gas compressor.SOLUTION: A gas compressor includes: a suction port 12a (opening) that is formed in a housing 10, and to which a low-pressure pipeline 120 (pipeline member) containing a pipeline part 122 is connected; and an O ring 12m (seal member) that is arranged between an insertion pipeline 122a of the pipeline 122 and the suction port 12a. In the gas compressor, among the connection surface (formed fine gap) between the low-pressure pipeline 120 and the suction port 12a, to the whole circumference around the insertion pipeline 122a in a range from the outside of the housing 10 to the O ring 12m, an annular space 12d (shielding part) preventing moisture having entered the fine gap from reaching the O ring 12m is provided.

Description

  The present invention relates to a gas compressor (compressor), and more particularly, to improvements such as a suction port to which a low-pressure pipe to which gas is supplied is connected and a discharge port to which a high-pressure pipe to which gas is discharged is connected. .

  Conventionally, a gas compressor having a compression chamber for compressing a gas such as a refrigerant gas into a high-pressure compressed gas is used in an air conditioning system (hereinafter referred to as an air conditioning system).

Here, in the gas compressor, a low pressure pipe to which a low pressure gas is supplied and a high pressure pipe from which a high pressure gas is discharged are connected to the housing.
The low-pressure pipe is a pipe that supplies a low-pressure gas from the outside of the gas compressor, for example, an evaporator, and the high-pressure pipe is a high-pressure gas that is compressed in the compression chamber of the gas compressor, such as the outside of the gas compressor. It is piping discharged to a condenser (patent document 1).

JP 2004-68781 A

An O-ring or the like is provided between each pipe described above and each opening such as a suction port and a discharge port in order to ensure airtightness between the inside and outside of the gas compressor.
Here, before the O-ring, moisture may enter due to a capillary phenomenon passing through a minute gap between the pipe and the opening.
Although this moisture is blocked by the O-ring and does not enter the inside of the housing, it stays in the vicinity of the O-ring and may cause corrosion by the oxygen concentration cell in the opening near the stayed portion. is there.
This invention is made | formed in view of the said situation, Comprising: It aims at providing the gas compressor which can prevent thru | or suppress corrosion of an opening.

The gas compressor according to the present invention is provided with a blocking portion that prevents moisture that has entered a minute gap formed between the piping member and the opening from traveling through the minute gap, thereby preventing corrosion of the opening. Thorough suppression.
That is, the gas compressor according to the present invention includes an opening formed in a housing to which a pipe member including a pipe is connected, and a seal member disposed between the pipe and the opening. Between the outside of the housing and the seal member in the minute gap formed between the opening and the opening, and the moisture that has entered the minute gap around the piping is the seal. A blocking part for preventing the member from reaching the member is provided.

  The gas compressor according to the present invention can prevent or suppress the corrosion of the opening.

It is a longitudinal section showing a vane rotary type compressor which is one embodiment of a gas compressor concerning the present invention. FIG. 2 is a detailed cross-sectional view showing a suction port (discharge port) of the compressor shown in FIG. 1. It is sectional drawing equivalent to FIG. 2 which shows other embodiment (Embodiment 2). It is sectional drawing equivalent to FIG. 2 which shows other embodiment (Embodiment 3). It is sectional drawing equivalent to FIG. 2 which shows other embodiment (Embodiment 4).

  Hereinafter, an embodiment according to the gas compressor of the present invention will be described with reference to the drawings.

(Embodiment 1)
(Constitution)
A vane rotary type compressor 100 (hereinafter simply referred to as a compressor 100), which is an embodiment of a gas compressor according to the present invention, compresses a supplied refrigerant gas G (gas) to a high pressure as shown in FIG. The compressor main body 60 is accommodated inside the housing 10.
The compressor 100 is configured as a part of an air conditioning system (hereinafter, simply referred to as an air conditioning system) that performs cooling using the heat of vaporization of a cooling medium, and includes a condenser and an expansion that are other components of the air conditioning system. Along with a valve, an evaporator, etc., it is provided on the circulation path of the cooling medium.

The compressor 100 compresses the refrigerant gas G as a gaseous cooling medium taken from the evaporator of the air conditioning system, and supplies the compressed refrigerant gas G to the condenser of the air conditioning system.
The condenser heat-exchanges the compressed refrigerant gas G with ambient air and the like to dissipate heat from the refrigerant gas G and liquefy it, and sends it to the expansion valve as a high-pressure liquid refrigerant.
The high-pressure liquid refrigerant is reduced in pressure by the expansion valve and sent to the evaporator. The low-pressure liquid refrigerant absorbs heat from ambient air and vaporizes in the evaporator, and cools the air around the evaporator by heat exchange accompanying the vaporization of the refrigerant.
The vaporized low-pressure refrigerant gas G returns to the compressor 100 and is compressed, and the above steps are repeated thereafter.

The housing 10 includes a case 11 having one end closed and the other end opened, and a front head 12 covering the other open end of the case 11. The front head 12 is attached to the case 11 by a fastening member such as a bolt. It is assembled.
With the front head 12 assembled to the case 11, a space is formed inside the housing 10, and the compressor body 60 is accommodated in the space.
The front head 12 is connected to a low-pressure pipe 120 (pipe member) connected from the evaporator to form a suction port 12a (suction port, opening) for taking in the low-pressure refrigerant gas G. A high-pressure pipe 110 (pipe member) connected to the condenser is connected to form a discharge port 11a (discharge port, opening) for discharging the high-pressure refrigerant gas G compressed by the compressor body 60.

  The suction port 12a is provided with a check valve for preventing the refrigerant gas G from flowing back from the inside of the housing 10 to the low-pressure pipe 120. However, the check valve is not shown in order to avoid complication. Yes.

The suction port 12a and the low pressure pipe 120 are connected in detail as shown in FIG.
That is, the low-pressure pipe 120 is provided with a flange part 121 for coupling to the suction port 12a with the bolt 16 near the tip of the pipe part 122 (pipe).
The piping portion 122 is divided into an insertion piping 122 a that protrudes to the tip side from the flange portion 121 and an exposed piping 122 b that is upstream from the flange portion 121.
The insertion pipe 122a is inserted into the suction port 12a and hidden inside the housing 10, as shown in FIG. 2, with the flange portion 121 coupled to the suction port 12a with the bolt 16.
On the other hand, the exposed pipe 122b is exposed to the outside of the housing 10 as shown in FIG. 2 in a state where the flange portion 121 is coupled to the suction port 12a with the bolt 16.

  Near the tip of the insertion pipe 122a, a groove is formed on the outer circumferential wall of the insertion pipe 122a, and an O-ring 12m (seal member) is fitted into the groove. The O-ring 12m is a groove of the insertion pipe 122a. Between the bottom surface of the housing 10 and the inner peripheral surface of the suction port 12a to ensure airtightness inside and outside the housing 10 at the suction port 12a.

In addition, a convex portion 121b (second convex portion) that protrudes toward the end surface 12c of the suction port 12a is formed on the opposing surface 121a of the flange portion 121 that faces the end surface 12c of the suction port 12a.
The convex portion 121b is formed outside the insertion pipe 122a over the entire circumference around the insertion pipe 122a.
On the other hand, the end surface 12c of the suction port 12a is formed with a convex portion 12b (first convex portion) protruding toward the flange portion 121 of the low-pressure pipe 120.
The convex portion 12b is also formed outside the insertion pipe 122a over the entire circumference around the insertion pipe 122a.
In the compressor 100 of this embodiment, the convex portion 121b of the low-pressure pipe 120 is formed outside the convex portion 12b on the outside of the convex portion 12b of the suction port 12a, but in the gas compressor according to the present invention, The convex portion 12b of the suction port 12a may be formed outside the convex portion 121b of the low pressure pipe 120.

The end surface (lower surface in the drawing) of the convex portion 121b of the low-pressure pipe 120 is in contact with the end surface 12c of the suction port 12a, and the end surface (upper surface in the drawing) of the suction port 12a is in contact with the opposing surface 121a of the low-pressure piping 120. ing.
The convex portion 121b of the low-pressure pipe 120 and the convex portion 12b of the suction port 12a are separated along the radial direction of the insertion pipe 122a.
Since this gap is also formed over the entire circumference around the insertion pipe 122a, an annular space 12d (a blocking portion, an annular space that blocks capillary action) is formed between the protruding portion 121b and the protruding portion 12b. Is formed.

  FIG. 2 shows the structure of the suction port 12a and the low-pressure pipe 120. As indicated by the reference numerals in parentheses, the structure of the discharge port 11a and the high-pressure pipe 110 in the past also includes the structure of the suction port 12a and the low-pressure pipe 120. The structure is the same.

The compressor main body 60 includes a rotating shaft 51, a rotor 50, a cylinder 40, a vane 58, a front side block 20, and a rear side block 30.
The rotary shaft 51 is driven to rotate about the axis C.
The rotor 50 is formed in a cylindrical shape and rotates integrally with the rotation shaft 51.
The cylinder 40 has an inner peripheral surface 41 having a substantially elliptical cross-sectional outline that surrounds the outer peripheral surface of the rotor 50 and is open at both ends.
The vane 58 is formed in a plate shape and is embedded in the rotor 50 so as to be able to protrude outward from the outer peripheral surface 52 of the rotor 50, and the tip on the protruding side follows the contour shape of the inner peripheral surface 41 of the cylinder 40. Thus, the amount of protrusion is variable, and it is arranged on the rotor 50 around the axis C at equal angular intervals.
For example, five vanes 58 are provided (may be two, three, four, etc. other than five).
The front side block 20 and the rear side block 30 are fixed so as to cover the open end surfaces from the outside of the open end surfaces on both sides of the cylinder 40, respectively.
The rear side block 30 is provided with an oil separator 70 that separates the refrigerating machine oil R (lubricating oil) from the refrigerant gas G.

The volume of the compression chamber 43, which is a space partitioned by two vanes 58 and 58 that follow each other along the rotation direction of the two side blocks 20 and 30, the rotor 50, the cylinder 40, and the rotation shaft 51, rotates. By repeating the increase / decrease according to the rotation of the shaft 51, the refrigerant gas G is sucked into the compression chambers 43 (intake stroke), the refrigerant gas G is compressed in the compression chambers 43 (compression stroke), and the compression chambers are compressed. The process of discharging the high-pressure refrigerant gas G from the inside 43 (discharge process) is repeated.
The compressor 100 is configured to perform a series of cycles of a suction stroke, a compression stroke, and a discharge stroke twice while the rotary shaft 51 rotates once.
Accordingly, the two suction strokes, the two compression strokes, and the two discharge strokes are set in ranges that are shifted from each other by a rotation angle of 180 degrees.

Inside the housing 10 is discharged from the suction chamber 13, which is a space through which the refrigerant gas G supplied through the suction port 12 a and sucked into the compression chamber 43 of the compressor body 60 passes, and the compression chamber 43 of the compressor body 60. A discharge chamber 14 which is a space through which the refrigerant gas G discharged through the port 11a passes is formed by the housing 10 and the compressor body 60, respectively.
The suction chamber 13 is a space surrounded by the front head 12 and the front side block 20 of the compressor main body 60, and partly a lip seal that seals the gap between the through hole of the front head 12 and the rotary shaft 51. A seal chamber 13 a provided with 53 is formed.
On the other hand, the discharge chamber 14 is a space surrounded by the case 11 and the rear side block 30 of the compressor body 60.

Refrigerating machine oil R separated from the refrigerant gas G by the oil separator 70 is stored at the bottom of the discharge chamber 14.
The refrigerating machine oil R includes oil passages 34 a and 34 b formed in the rear side block 30 of the compressor main body 60 by the high pressure of the refrigerant gas G discharged into the discharge chamber 14, an oil passage 44 formed in the cylinder 40, and the front side. Through the oil passage 24 formed in the block 20, it is supplied as a back pressure that causes the vane 58 to protrude outward.

(Function)
According to the compressor 100 of the present embodiment configured as described above, the relatively low-pressure refrigerant gas G supplied to the suction port 12a through the low-pressure pipe 120 is introduced from the suction chamber 13 into the compression chamber 43 of the compressor body 60. The refrigerant gas G compressed in the compression chamber 43 along with the rotation of the rotating shaft 51 and having a relatively high pressure in the compression chamber 43 is separated from the refrigerating machine oil R by the oil separator 70, and is discharged into the discharge chamber 14. It flows and is discharged from the discharge port 11a to the outside of the housing 10 through the high-pressure pipe 110.

  Here, the suction port 12a and the low-pressure pipe 120 are fastened by the bolt 16, but between the end face 12c of the suction port 12a, which is a joint surface by this fastening, and the opposing surface 121a of the flange portion 121 of the low-pressure pipe 120. Moisture may enter a minute gap (a gap enough to cause a capillary phenomenon) from the outside of the convex portion 121b of the low-pressure pipe 120 due to the capillary phenomenon.

However, the minute gap between the end surface 12c of the suction port 12a and the opposing surface 121a of the convex portion 121b of the low-pressure pipe 120 is an annular shape that does not cause capillary action until it reaches the insertion pipe 122a. Therefore, moisture that has passed through a minute gap between the end surface 12c of the suction port 12a and the opposing surface 121a of the convex portion 121b of the low-pressure pipe 120 is accumulated in the annular space 12d and is inserted into the insertion pipe 122a. The O-ring 12m is not reached.
Therefore, in the suction port 12a, corrosion caused by moisture that has entered can be prevented or reduced at a portion where the O-ring 12m provided on the insertion pipe 122a contacts or in the vicinity thereof.
By preventing corrosion of the suction port 12a, it is possible to prevent leakage of the refrigerant gas G from a portion where the O-ring 12m contacts.

  Note that the compressor 100 of the present embodiment has a joint surface between the facing surface 121a of the flange portion 121 and the convex portion 12b inside the space 12d that hinders capillary action that causes moisture intrusion, that is, an O-ring than the space 12d. The joint surface on the side close to 12 m is higher in the vertical direction than the joint surface outside the space 12 d (the joint surface between the convex portion 121 b of the flange portion 121 and the end surface 12 c of the suction port 12 a). The water surface in the space 12d of the water that has entered the space 12d from the joint surface outside 12d reaches the joint surface inside the space 12d (joint surface between the facing surface 121a of the flange 121 and the convex portion 12b). There is nothing.

  In the compressor 100 of the present embodiment, the connection portion between the discharge port 11a and the high-pressure pipe 110 has the same configuration as the connection portion between the suction port 12a and the low-pressure pipe 120, and thus the connection between the suction port 12a and the low-pressure pipe 120 described above. The effect of preventing the corrosion of the suction port 12a due to the capillary phenomenon at the portion is also exhibited in the connection portion between the discharge port 11a and the high-pressure pipe 110, and the discharge port 11a can be prevented or reduced.

The compressor 100 according to the present embodiment applies a structure for preventing or reducing corrosion to both the suction port 12a and the discharge port 11a. However, the gas compressor according to the present invention is limited to this form. Instead, the above structure may be applied only to the suction port 12a or only to the discharge port 11a.
In comparison between the suction port 12a and the discharge port 11a, the suction port 12a is more likely to cause water intrusion due to the fact that the water does not easily evaporate at a lower temperature than the discharge port 11a. It is preferable to apply the above structure to the suction port 12a in preference to the above.

(Embodiments 2 and 3)
In the embodiment described above, the compressor 100 also has a space 12d in the low pressure pipe 120 that cuts off the capillary phenomenon in which moisture enters between the joint surfaces of the low pressure pipe 120 and the high pressure pipe 110 in the suction port 12a and the discharge port 11a. Although it is formed by a combination of the convex portion 121b and the convex portion provided on the end surface 12c of the suction port 12a, the space 12d is not limited to this form.
That is, for example, as shown in FIG. 3, the space 12d may be formed by an annular groove (Embodiment 2) around the entire circumference of the insertion pipe 122a of the end surface 12c of the suction port 12a.
On the other hand, for example, as shown in FIG. 4, the space 12d is formed by an annular groove (Embodiment 3) around the entire circumference of the insertion pipe 122a of the facing surface 121a of the flange 121 of the low-pressure pipe 120. May be.

(Embodiment 4)
In the compressor 100 of each embodiment described above, the space 12d that cuts off the capillary phenomenon in which moisture enters between the joint surfaces of the low-pressure pipe 120 and the high-pressure pipe 110 to the suction port 12a and the discharge port 11a, and the path of the joint surface. Although it is an example provided above, the gas compressor concerning the present invention is not limited to this form.
That is, as shown in FIG. 5, for example, as a blocking portion that cuts off the capillary phenomenon in which moisture enters the suction port 12 a between the joint surface with the low-pressure pipe 120, a path through which moisture passes through the capillary phenomenon (the joint surface). An O-ring 12n (second seal member) different from the O-ring 12m on the upstream side of the existing O-ring 12m in the gap between the end surface 12c of the suction port 12a and the opposing surface 121a of the flange 121. It is also possible to apply a configuration provided with

In this way, by providing another O-ring 12n upstream of the existing O-ring 12m, a capillary phenomenon causes a gap between the end surface 12c of the suction port 12a and the facing surface 121a of the flange portion 121. Moisture that has entered the gap is prevented from progressing to the O-ring 12m by the O-ring 12n that is added before reaching the existing O-ring 12m, so that corrosion in the vicinity of the existing O-ring 12m is prevented or reduced. can do.
The moisture that has entered the gap due to the capillary phenomenon stays in the vicinity of the added O-ring 12n, and thus may corrode the vicinity of the O-ring 12n, but even if the vicinity of the O-ring 12n corrodes. Since the refrigerant gas G does not leak unless the portion near the other O-ring 12m is corroded, the probability of the refrigerant gas G leaking can be significantly reduced.

Furthermore, when the insertion pipe 122a is applied as an arrangement position of the additional O-ring 12n in the same manner as the existing O-ring 12m, it is necessary to newly form a groove for preventing the O-ring 12n from dropping off in the insertion pipe 122a. However, for example, as shown in FIG. 5, by adopting a configuration in which an O-ring 12n is arranged in a chamfered portion 12f formed in advance at a portion where the end surface 12c of the suction port 12a and the inner peripheral surface 12e intersect. It is not necessary to form the new groove described above.
In addition, according to the configuration in which the O-ring 12n is disposed in the chamfered portion 12f, moisture that has entered the gap between the end surface 12c of the suction port 12a and the facing surface 121a of the flange portion 121 due to capillary action is the end surface 12c that is a horizontal plane. However, it does not reach the inner peripheral surface 12e, which is a vertical surface.
Since moisture easily diffuses in a horizontal plane, it does not stay as much as in the vertical plane. Therefore, according to the compressor 100 of the second embodiment, corrosion itself caused by moisture retention can be made difficult to occur.

10 Housing 11a Discharge port (opening)
12a Suction port (suction port, opening)
12b Convex part (first convex part)
12d space (blocking part, space)
12m O-ring (seal member)
12n O-ring (second seal member)
100 compressor (gas compressor)
110 High-pressure piping (piping members)
120 Low pressure piping (piping material)
111, 121 Flange part 112, 122 Piping part (piping)
112a, 122a Insertion pipe 121b Convex part (second convex part)
C Center axis G Refrigerant gas (gas)
R refrigerator oil

Claims (7)

An opening formed in the housing to which a piping member including piping is connected, and a seal member disposed between the piping and the opening;
Of the minute gap formed between the pipe member and the opening, moisture that has entered the minute gap in the entire circumference around the pipe in a range from the outside of the housing to the seal member The gas compressor which provided the interruption | blocking part which prevents that reaches | attains the said sealing member.   2. The gas compressor according to claim 1, wherein the blocking portion is an annular space formed in a part of the minute gap and blocking a capillary phenomenon. An annular first convex portion is formed around the opening,
An annular second convex portion is formed at a position away from the first convex portion of the piping member,
The gas compressor according to claim 2, wherein the annular space is a space formed between the first convex portion and the second convex portion.   The gas compressor according to claim 3, wherein the second convex portion is formed outside the first convex portion. An annular groove is formed around the opening or in the pipe,
The gas compressor according to claim 2, wherein the annular space is the groove.   2. The gas compressor according to claim 1, wherein the blocking portion is a second seal member provided over an entire circumference around the pipe in any range from the outside of the housing to the seal member. .   The gas compressor according to any one of claims 1 to 6, wherein the opening is a suction port that supplies gas into the housing.